JP3679749B2 - Hydraulic device - Google Patents

Hydraulic device Download PDF

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Publication number
JP3679749B2
JP3679749B2 JP2001356727A JP2001356727A JP3679749B2 JP 3679749 B2 JP3679749 B2 JP 3679749B2 JP 2001356727 A JP2001356727 A JP 2001356727A JP 2001356727 A JP2001356727 A JP 2001356727A JP 3679749 B2 JP3679749 B2 JP 3679749B2
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Japan
Prior art keywords
control valve
hydraulic
drive source
value
detecting means
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Expired - Fee Related
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JP2001356727A
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Japanese (ja)
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JP2003130006A (en
Inventor
鈴木　　茂
浩一 青山
悟 島田
純子 関
孝彦 伊東
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Yukigaya Institute Co Ltd
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Yukigaya Institute Co Ltd
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Priority to JP2001356727A priority Critical patent/JP3679749B2/en
Priority to TW091122205A priority patent/TW539812B/en
Priority to CA002473966A priority patent/CA2473966C/en
Priority to MXPA04003557A priority patent/MXPA04003557A/en
Priority to PCT/JP2002/010849 priority patent/WO2003036100A1/en
Priority to EP02775375A priority patent/EP1439310A4/en
Priority to CNB028252535A priority patent/CN100404881C/en
Priority to AU2002344002A priority patent/AU2002344002B8/en
Priority to US10/492,978 priority patent/US7043906B2/en
Publication of JP2003130006A publication Critical patent/JP2003130006A/en
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Publication of JP3679749B2 publication Critical patent/JP3679749B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/265—Control of multiple pressure sources
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31594—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having multiple pressure sources and multiple output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

【技術分野】
【０００１】
慣性を具備した駆動源により駆動される油圧ポンプの油圧により駆動される負荷と、制御弁の切替動作により発生する圧力が上昇した作動油を供給する装置と、フライホイールあるいは油圧蓄積装置に代表されるエネルギ蓄積装置との間で油圧作動流体を媒体として、エネルギの供給または回収を行うことにより、負荷が要求するエネルギ量を制御する油圧装置に関する。
【背景技術】
【０００２】
低圧油圧源を持つ油圧装置においては、負荷が必要とする作動油量が変化する場合には、吐出される作動油が一定のため、余剰作動油が発生してしまう。したがって、負荷が必要とする作動油のみを供給する制御を行わなければならない。そのために油圧源の回転数を変えるか、絞り弁や減圧弁等で流量調整することが行われている。駆動源、油圧ポンプにおいて、全ての回転領域で高効率を維持することは困難であり、回転数を変えることは効率を悪化させる要因となる。また、流量調整することも熱エネルギとして損失させながら消費しているに過ぎず効率を悪化させる要因となっている。
【０００３】
また、上記問題を解決するために可変吐出量ポンプが使用されているが、このポンプは構造が複雑で高価である。また、駆動源である熱機関または電動機等の原動機の軸出力を必要に応じて変化させなければならず、全ての領域で高効率を維持することは困難である。さらに、吐出圧力、油量の変更、調整を適時行うことは多大な制御設備が必要であり、コスト面でも不利となっている。
【０００４】
ポンプをモータとして広範囲の回転数で動作させることは、定吐出量ポンプでは可能であるが、可変吐出量ポンプでは困難である。よって車両等の駆動系として可変吐出量ポンプを搭載した場合は、可逆的な制御を行うことはできない。
【発明の開示】
【発明が解決しようとする課題】
【０００５】
本発明では、駆動源である熱機関または電動機等の原動機を最も効率の良い回転数付近で使用し、定吐出量、可変吐出量ポンプのようなポンプの形式を問わず、常に効率の良い回転数で動作させた状態において、外部の制御弁を要求される動作に応じて切り替えることによって、高圧小流量から低圧大流量の作動油を高効率で負荷へ供給することを課題とする。
【０００６】
また、制御弁の開閉切替動作により、定吐出量ポンプで可変吐出量ポンプのような制御をすることを課題とする。
【課題を解決するための手段】
【０００７】
上記課題を解決するために本発明においては、所要量の慣性を内在または付加により具備した駆動源と、この駆動源によって駆動される油圧ポンプと、この油圧ポンプの吐出側に接続された第１の制御弁と、この第１の制御弁の通過側を作動油タンクへ導く流路と、前記油圧ポンプの吐出側に入力側を向けた逆止弁と、この逆止弁の出力側に管路を介して設けられた第１のエネルギ蓄積装置と、この第１のエネルギ蓄積装置と前記逆止弁との間の管路から分岐された管路に接続された負荷を、前記第１の制御弁の開閉動作の切り替えを行う制御回路とを備え、前記駆動源４１が発生するトルクをＱｍ、前記第１の制御弁が阻止側に切り替えられた状態にある場合の油圧ポンプのトルクをＱｐ、前記駆動源の軸周りの慣性モーメントを１、角速度をω、および前記駆動源が有する慣性トルクをＩ・ｄω／ｄｔとしたときに、Ｑｐ＝Ｑｍ−Ｉ・ｄω／ｄｔの関係式において、Ｑｐの値がＱｍの値を超える値にあり、前記制御回路により前記第１の制御弁を通過側、阻止側の状態に切り替える動作を反復させ、前記駆動源の角速度ωの値を自励振動動作させることで、前記駆動源の回転数が減速することで得られる慣性トルクが、前記駆動源の出力トルクに付加されたトルクで前記油圧ポンプを駆動したときに圧力上昇した作動油を前記負荷に連続的に供給することを特徴とする油圧装置を手段として用いる。
【０００８】
他の実施例においては、前記駆動源の回転数を検知する回転検知手段を備え、前記回転検知手段の値が下限設定値まで減少したとき前記制御回路により前記第１の開閉弁を通過側の状態に切り替え、前記回転検知手段の値が上限設定値まで増大したとき前記制御回路により前記第１の制御弁を阻止側の状態に切り替え、これらの動作を反復させることを特徴とする請求項１記載の油圧装置を手段として用いる。
【０００９】
他の実施例においては、前記駆動源の回転数を検知する回転検知手段を備え、前記回転検知手段の値に応じて前記第１の制御弁の反復切り替えを行うタイミングを決定する前記制御回路により、前記第１の制御弁が通過側、阻止側の状態に反復切り替えさせることを特徴とする請求項１記載の油圧装置を手段として用いる。
【００１０】
他の実施例においては、前記逆止弁の出力側に設けられた圧力検知手段を備え、この圧力検知手段の値が上限設定値まで増大したとき前記制御回路により前記第１の制御弁１を通過側の状態に切り替え、前記圧力検知手段の値が下限設定値まで減少したとき前記制御回路により前記第１の制御弁を阻止側の状態に切り替え、これらの動作を反復させることを特徴とする請求項１記載の油圧装置を手段として用いる。
【００１１】
他の実施例においては、前記逆止弁の出力側に設けられた圧力検知手段を備え、この圧力検知手段の値に応じて前記第１の制御弁の反復切り替えを行うタイミングを決定する前記制御回路により、前記第１の制御弁が通過側、阻止側の状態に反復切り替えさせることを特徴とする請求項１記載の油圧装置を手段として用いる。
【００１２】
前記第１のエネルギ蓄積装置と前記逆止弁との間の管路から分岐された管路に接続され、下流側に前記負荷が設けられた第２の制御弁と、この第２の制御弁と前記負荷との間の管路から分岐した管路に作動油タンクへ入力側を向けた逆止弁とを備え、前記第２の制御弁を通過側、阻止側の状態に切り替える動作を反復させ、前記負荷の必要油量が油圧ポンプの供給油量より多いとき、間欠的に前記負荷を加速することを特徴とする請求項１から５記載のうちいずれか１項に記載の油圧装置を手段として用いる。
【発明の効果】
【００１３】
本発明では、定圧油圧源から吐出される作動油を、制御弁を要求される負荷に応じて切り替えることによって、高圧小流量から低圧大流量まで、効率良く負荷へ供給できるので、駆動源である熱機関または電動機等の原動機を最も効率の良い回転数付近で使用することができ、また、駆動される油圧ポンプも、定吐出量、可変吐出量ポンプのような形式を問わず、常に効率の良い回転数で動作させることができるので、従来の素子を能率良く動作させることができ、システム全体の効率をより高くすることができる。
【００１４】
また、この動作によれば、従来の定吐出量ポンプで余剰として捨てていたエネルギの損失もなくなるため、作動油の温度上昇や劣化を防止することができ、可変吐出量ポンプとしての動作も、ポンプで容量を可変することなく実現できるので、高価な可変吐出量ポンプを使用せずに定吐出量ポンプで可変吐出量ポンプと同じ機能を実現できる。
【００１５】
また、本発明の油圧装置を車両等の駆動装置として使用した場合は、走行する車両等が持つ運動エネルギを回収することで回生制動を実現したり、駆動源である原動機をエンジンブレーキとして機能させたりと、ポンプモータの可逆的動作が自在となり、効率が高い運転が可能である。また、回生しない場合には作動油の温度上昇を防ぐことができる。
【発明を実施するための最良の形態】
【００１６】
図１は、本発明の油圧装置の構成要素と、それらを結合する流路による油圧回路を示す図である。図１において、４１は駆動源であって、主として熱機関であるが、他の形式のものでも採用できる。駆動源４１の軸２０１には慣性体、具体的にはフライホイール４５が取り付けられ、さらに軸２０２により油圧ポンプ１１を駆動する。駆動源自体が大きな慣性モーメントを有する場合、慣性が内在されている場合には、外付けのフライホイール４５は省略することができる。図１は、油圧装置のシステム全体を示しており、複数の異なる機能、動作を担当する部分が有機的に結合されている。なお、油圧ポンプ１１は、後述するが本油圧装置において、モータの機能も兼ねる第３のポンプモータをも構成する。
【００１７】
油圧ポンプ１１の吐出側には管路１０５が接続されており、管路１０５には分岐した管路１０６が連通し、各請求項の第１の制御弁を構成する制御弁１を介して作動油タンク２１へ導く管路１０７が接続されている。駆動源４１を始動し、油圧ポンプ１１があらかじめ設定された回転数、すなわち設定回転数で運転している状態において、作動油は作動油タンク２１から管路１０１、フィルタ２２、管路１０２、逆止弁２３を経由して油圧ポンプ１１の流入側の管路１０４に至る流路で油圧ポンプ１１へ吸入される。
【００１８】
吸入された作動油は、油圧ポンプ１１により吐出され、吐出側の管路１０５から、管路１０６、制御弁１の通過側１ａ、管路１０７を通過して作動油タンク２１に流れる。制御弁１が通過側１ａに切り替えられている状態では、管路１０６以降はアンロード流路を形成する。
【００１９】
この状態で、制御弁１を通過側１ａから阻止側１ｂに切り替えると、駆動源４１で駆動される油圧ポンプ１１によって衝撃的に圧力上昇した作動油が、管路１０５、１０８を通って入力側を向けて接続された逆止弁２４を通過し、逆止弁２４の出力側に接続された負荷に供給される。このように、制御弁１の通過側１ａから阻止側１ｂの切り替え時には、駆動源４１により設定回転数で運転される油圧ポンプ１１が連続的に発生できる吐出圧力、すなわち油圧ポンプ１１の通常運転時に吐出する圧よりも高い圧力が発生する。
【００２０】
駆動源４１は熱機関または電動機等の原動機で、発生可能なトルクがＱｍであるとき、駆動源により駆動される油圧ポンプ１１のトルクをＱｐとすると、損失を無視した場合には、Ｑｍ＝Ｑｐの関係が成立することは明らかである。ここで駆動源４１の慣性モーメントをＩ、角速度をωとすると、駆動源が加速または減速する際に要する慣性トルクはＩ・ｄω／ｄｔで表せる。なお、Ｉ・ｄω／ｄｔは加速時には＋、減速時には−の値をもつことになる。
【００２１】
本発明の装置は、制御弁１が通過側１ａの状態にある場合には、駆動源４１は設定された回転を維持するように制御される。制御弁１が阻止側１ｂに切り替えられたときは、駆動源４１の慣性トルクＩ・ｄω／ｄｔがＱｍに加算されることとなり、Ｑｐ＝Ｑｍ−Ｉ・ｄω／ｄｔの関係が成立する。よって、減速による慣性のトルクが付加されることにより、通常運転時の油圧ポンプ１１の入力トルクＱｍよりも大きい出力トルクが得られ、その結果圧力が上昇した作動油を負荷に供給することができる。
【００２２】
これまでの説明は、制御弁１を通過側１ａから阻止側１ｂに切り替える動作を１回だけ行った場合についてのみであったが、阻止側１ｂから通過側１ａに切り替え、再び阻止側１ｂに切り替える動作（切替動作）を反復することにより、上記のように高い圧力の作動油を負荷に連続的に供給することができる。
【００２３】
このように、本発明では、より小さい駆動源で高い油圧を供給できるので、負荷が必要とする最大負荷トルクに合わせた出力トルクを持つ駆動源を設けることなく、駆動させることが可能であり、経済的にも大きなメリットがある。発生できる最大圧力は、駆動源４１の慣性モーメントＩと角加速度ｄω／ｄｔの大きさによって設定することができる。
【００２４】
制御弁１の切替動作は、次のように行われる。図１において、フライホイール４５には回転計４９が設けられ、駆動源４１の回転数は、この回転計４９によって検出される。また、逆止弁２４の出力側には圧力センサ３３が設けられている。前記油圧ポンプ１１の負荷トルクが駆動源４１の出力トルクを越え、その結果回転数が低下して回転数の下限設定値にまで減少したことは、回転計４９によって検出できる。
【００２５】
回転数が下限設定値以下になったら、制御弁１を通過側１ａに切り替えて、アンロード状態、すなわち油圧ポンプ１１の負荷を除去した状態とする。その結果、駆動源４１にかかる負荷トルクが減少して、その回転数が次第に増加し、上限設定値以上になる。このとき再び、制御弁１を阻止側１ｂに切り替える動作を行う。この切替動作は、上限設定値に達した瞬間でも後でも設定値に達することを予測して達する若干前でも可能であるのは言うまでもない。このようにして、制御弁１は切替動作を繰り返し実行して自励動作を持続させる。油圧ポンプ１１の回転数変化、すなわち作動油吐出量の変化の速さは油圧ポンプ１１の軸の周りの慣性モーメントに依存する。
【００２６】
また、圧力センサ３３は、逆止弁２４の出力側の圧力状態を測定する。圧力センサ３３の測定値が所定の設定値に到達したら、制御弁１を阻止側１ｂから通過側１ａに切り替えて、油圧ポンプ１１から吐出された作動油を作動油タンク２１へ戻す。この動作により原動機の負荷がアンロード状態となり、回転数が増加する。このように切り替えのタイミングを決定するために使用するセンサは、圧力センサ３３や回転計４９のような各請求項を構成する検知手段や、負荷の状態を監視するセンサ、あらかじめ切り替えるタイミングが分かっている場合等は状態を監視することなく外部からのクロックタイミングに応じて行うことも可能である。
【００２７】
逆止弁２４の出力側には、管路１０９，１１０を介して設けられた第１のエネルギ蓄積装置３１と、この第１のエネルギ蓄積装置３１と逆止弁２４との間の管路１１５，１１６に設けられた各請求項の第２の制御弁を構成する制御弁２と、制御弁２の下流側に設けられた負荷１２とが備わっている。この負荷１２は、実施例においては、第２のエネルギ蓄積装置４２を設けた油圧モータ１２であり、第２のエネルギ蓄積装置４２の具体的な装置としては、油圧モータ１２に取り付けられたフライホイールである。なお、油圧モータ１２は、後述するが本油圧装置においてポンプの機能も兼ねる各請求項の第２のポンプモータをも構成する。
【００２８】
制御弁２が通過側２ａに切り替えられている時、駆動源４１によって駆動される油圧ポンプ１１とエネルギ蓄積装置としてのアキュムレータ３１から作動油が油圧モータ１２に流入し、吐出側の管路１２４から分岐した作動油タンク２１へ通じる管路途中の制御弁４を経由して作動油タンク２１へ戻される。この動作により油圧モータ１２に設けられたフライホイール４２は加速される。
【００２９】
制御弁２と油圧モータ１２との間には、作動油タンク２１へ入力側を向けて接続した逆止弁２６が設けられた管路１２０，１２１，１２２が設けられている。その理由について図２を参照して説明する。この図２は図１から説明のための主要な要素を抜き出したものである。油圧モータ１２の回転数が増加し、油圧モータ１２の必要油量が油圧ポンプ１１の供給油量より多くなった場合には、油圧モータ１２を加速することができなくなる。
【００３０】
このとき、制御弁２を通過側２ａから阻止側２ｂに切り替える。この動作により、アキュムレータ３１には作動油が蓄積され、油圧モータ１２は逆止弁２６によりフリーホイリング状態となる。アキュムレータに所定量の作動油が蓄積されたら制御弁２を再び通過側２ａに切り替えると、蓄積された作動油が油圧モータ１２に流入し、油圧モータ１２は加速されることになる。このように、制御弁２の切替動作を反復することで油圧モータ１２の必要油量が油圧ポンプ１１の供給油量より多いときでも間欠的に加速をすることができる。よって加速平均圧力は低いが、大流量を負荷へ供給することが可能になる。
【００３１】
次に本発明の油圧装置を車両の駆動装置として使用する場合について説明する。図１において、油圧モータ１２の吐出側には管路を通じて入力側を向けて接続された逆止弁２７、この出力側にはアキュムレータ３４および制御弁５が設けられている。逆止弁２７の出力側にも圧力センサ３６が設けられている。逆止弁２７の出力側の管路１２８，１２９間には油圧ポンプ１１の流入側の管路１０３，１０４に連通した制御弁６を持つ管路１６０，１６１が分岐して連通されている。なお、制御弁６は、フライホイール４２があらかじめ設定された回転数で動作している場合、開閉動作を行うことでポンプモータ１２によりポンプモータ１１へ作動油を供給し、駆動源４１を起動させる等の動作を行うために使用する。
【００３２】
制御弁５の下流側にある１３，１４は第１のポンプモータを構成するポンプモータであり、ポンプモータ１３，１４に接続された４３，４４は、これらによって駆動される車両等の車輪を簡略化して示したものである。これらポンプモータ１３，１４が接続される制御弁７は車両の進行方向を制御するものである。制御弁５と制御弁７間の管路１３６，１３８には、駆動源４１から車両を直接駆動するために設けられた管路１１７，１１８、制御弁３および管路１３７が接続されている。
【００３３】
ポンプモータ１３，１４の吐出側には、吐出される作動油を作動油タンク２１へ戻すため管路１５５、第３の制御弁を構成する制御弁８および管路１５７が接続されている。管路１５５に接続された管路１５８には逆止弁３０が入力側を向けて接続されている。
【００３４】
このように構成された車両において、まず発進と加速動作を説明する。発進は加速する初速度が零の場合であり、加速は走行中に加速力を与えるものであるから、今後は両者を単に加速として説明する。車両を加速する場合には、駆動源４１のみを利用する場合、あらかじめ設定された回転数で動作しているフライホイール４２のみを利用する場合および駆動源４１とフライホイール４２との両方を利用する場合の３つのケースがある。
【００３５】
駆動源４１のみで車両の加速を行う場合の制御動作は、制御弁２，５，６および、逆止弁３０の出力側から管路１６１へのバイパス管路途中の制御弁９を阻止側に、制御弁８を通過側８ａに切り替えた状態で、制御弁３を通過側３ａに固定し、制御弁１を通過側１ａ、阻止側１ｂに状況に応じて繰り返し切替動作を行う場合と、制御弁１を阻止側１ｂに固定し、制御弁３を通過側３ａ、阻止側３ｂに状況に応じて繰り返し切替動作を行う場合、および制御弁１，３の双方を必要に応じて切替動作を行う場合の、さらに３つのケースがある。ただし制御弁５は状況に応じて切替を可能とする。また、図には記載しない制御弁を管路１３８部に配置し、上記内容と同様な操作を行っても加速動作は可能である。
【００３６】
フライホイール４２のみで加速する場合は、予め設定された範囲内で動作しているフライホイール４２が駆動側となり、これによって被駆動側である車両の加速を行う場合の制御動作は、少なくとも制御弁３，６および９を阻止側に、制御弁８を通過側８ａとした状態で、制御弁５を通過側５ａに固定し、制御弁４を通過側４ａ、阻止側４ｂに状況に応じて繰り返し切替動作を行う場合と、制御弁４を阻止側４ｂに固定し、制御弁５を繰り返し切替動作を行う場合、および制御弁４、５の双方を繰り返し切替動作を行う場合の、前欄と同様３つのケースがある。
【００３７】
また、駆動源４１、フライホイール４２の双方で車両を加速する場合でも、上記のように制御弁を状況に応じて繰り返し切替動作を行うことで可能となる。
【００３８】
ここで、制御弁の状況に応じた切替動作について説明する。車両の速度に応じて作動油の量は変化するが、その量は被駆動側のポンプモータ１３，１４の回転数等の状態を検知することにより判断でき、供給できる油量も同様に駆動側ポンプモータ１１または１２の回転数等を検知することで判断できる。それぞれの状態を検知する手段は、回転状態を検知する場合は、フライホイール４２に設けられたセンサ４６，ポンプモータ１３，１４に設けられたセンサ４７，４８およびフライホイール４５に設けられたセンサ４９等で行う。また、作動油の状態を検知する場合は、センサ３３，３６等によって行われる。これらの検知された値に応じて切替動作が行われることとする。なお、流量の測定は流量センサ等でも可能である。
【００３９】
例えば、センサ３６が予め設定された上限圧力に達したら、制御弁４を通過側４ａに切り替え、予め設定された下限圧力に達したら、再度制御弁４を阻止側４ｂへ切り替え、この切替動作の反復により加速を行う。このように、上限、下限圧力設定値を変えることで、加速度を制御できる。なお、予め駆動側、被駆動側の状態が把握できている場合は、別途設けられた制御回路から出力される制御信号やクロックにより制御弁を切替えることも可能である。
【００４０】
車両を加速させる作動油は、図１において油圧ポンプ１１から制御弁３を通過してポンプモータ１３，１４に流入し、制御弁８の通過側８ａを経由して作動油タンク２１へ排出される。また、油圧モータ１２に取り付けられたフライホイール４２が回転している状態では、ポンプモータ１２を油圧ポンプとして動作させて、作動油タンク２１から吐出側の管路を経由してアキュムレータ３４を蓄積し、その作動油を用いて駆動することもできる。
【００４１】
次に車両を惰行状態とする場合を説明する。この場合は、少なくとも制御弁３、５および６は阻止側で、制御弁８を通過側８ａに切り替えた状態であれば、管路１３８，１４２間に連通した、作動油タンク２１へ入力側を向けて接続した逆止弁２９が設けられた管路１３９、１４０、１４１がポンプモータ１３、１４のフリーホイリング回路となり、作動油は制御弁７，８を経由して、作動油タンク２１へ戻される。この状態で車両は惰行状態となる。なお、制御弁７を図１に記載されたタイプ以外のものを使用し、ポンプモータ１３、１４管路部を閉回路として構成することで、惰行させることも可能である。
【００４２】
最後に車両を減速する場合を説明する。減速動作には、回生を伴う減速動作と回生が伴わない減速動作の２つのパターンがある。まず回生の伴う減速動作について説明する。ポンプモータ１３，１４の吐出側に入力側を向けて接続された逆止弁３０の出力側が制御弁２の入力側に接続されている。これによって駆動側は、ポンプモータ１３，１４となり、被駆動側は、フライホイール４２が駆動される第２のポンプモータ１２となってフライホイール４２が加速されることによりこれが負荷となり車両の減速を行う。なお、制御動作については、フライホイール４２から車両を加速する場合と同様で、切り替える制御弁５と制御弁４はそれぞれ制御弁２と制御弁８になって同様の動作を行うことで説明できる。
【００４３】
次に回生を伴わない減速動作について説明する。図３は車両の持つ運動エネルギの回生を伴わないで減速させるために必要な回路構成を図１から抜き出したものである。この構成において動作を説明すると、車両が減速する場合、ポンプモータ１３，１４から吐出した作動油は、モータとして動作するポンプモータ１１に流入する。ポンプモータ１１は駆動源４１に連結されているから、いわゆるエンジンブレーキとして動作し、車両を減速させる。なお、制御動作は、前述したフライホイール４２から車両を加速する場合と同様で、切り替える制御弁５と制御弁４は、それぞれ制御弁９と制御弁８になって同様の動作を行うことで説明できる。
【００４４】
車両の減速時における回生動作については、前述したエネルギ蓄積装置またはフライホイール等で行うことが可能である。特に回生を必要としない場合でも、ポンプモータ１３，１４から吐出される作動油は、ポンプモータ１１に流入されることで、ポンプモータ１１が連結した原動機が負荷となりエネルギが消費されるため、リリーフ弁等で熱エネルギとして消費させることなく減速できるから、作動油の温度上昇や劣化を防止することができる。
【００４５】
本発明によれば、ポンプモータ１１，１２，１３および１４は、定吐出量ポンプによっても動作させることが可能であり、可変吐出量ポンプでは実現できない可逆動作も可能となることで、駆動側の原動機等のエンジンブレーキ作用を利用することができるようになる。
【００４６】
なお、本発明を実施形態に基づき具体的に説明したが、本発明は上記実施形態に限定されるものでなく、本発明で要求される機能を満足する素子であれば、置き換えが可能である。
【図面の簡単な説明】
【図１】 本発明の油圧装置の構成要素および油圧回路を示す図である。
【図２】 本発明の油圧ポンプを低圧大流量で動作させる装置の構成を図１から抜き出して示す図である。
【図３】 本発明を車両等の減速に運用した構成要素および油圧回路を図１から抜き出して示す図である。
【符号の説明】
１乃至９…制御弁、１１，１２，１３，１４…ポンプモータ、３１，３４…エネルギ蓄積装置またはアキュムレータ、３３…圧力センサ、４１…駆動源あるいは原動機、４２…フライホイール、４５…内在または外部付加の慣性体、４６乃至４９…回転計【Technical field】
[0001]
A load driven by the hydraulic pressure of a hydraulic pump driven by a drive source having inertia, a device for supplying hydraulic fluid with an increased pressure generated by a control valve switching operation, a flywheel or a hydraulic storage device The present invention relates to a hydraulic device that controls the amount of energy required by a load by supplying or recovering energy using a hydraulic working fluid as a medium with the energy storage device.
[Background]
[0002]
In a hydraulic device having a low-pressure hydraulic source, when the amount of hydraulic oil required by the load changes, surplus hydraulic oil is generated because the discharged hydraulic oil is constant. Therefore, it is necessary to perform control to supply only the hydraulic oil required by the load. For this purpose, the rotational speed of the hydraulic pressure source is changed or the flow rate is adjusted by a throttle valve, a pressure reducing valve, or the like. In a drive source and a hydraulic pump, it is difficult to maintain high efficiency in all rotation regions, and changing the number of rotations becomes a factor that deteriorates efficiency. In addition, adjusting the flow rate is only consumed while losing heat energy, and is a factor of deteriorating efficiency.
[0003]
In order to solve the above problem, a variable discharge pump is used, but this pump has a complicated structure and is expensive. Further, the shaft output of a prime mover such as a heat engine or electric motor as a drive source must be changed as necessary, and it is difficult to maintain high efficiency in all regions. In addition, timely change and adjustment of the discharge pressure and oil amount require a large amount of control equipment, which is disadvantageous in terms of cost.
[0004]
Although it is possible with a constant discharge pump to operate the pump as a motor at a wide range of rotation speeds, it is difficult with a variable discharge pump. Therefore, when a variable discharge pump is mounted as a drive system for a vehicle or the like, reversible control cannot be performed.
DISCLOSURE OF THE INVENTION
[Problems to be solved by the invention]
[0005]
In the present invention, a prime mover such as a heat engine or an electric motor as a driving source is used in the vicinity of the most efficient rotation speed, and the rotation is always efficient regardless of the type of pump such as a constant discharge amount or variable discharge amount pump. It is an object to supply high-efficiency low-flow-rate and high-flow-rate hydraulic oil to a load with high efficiency by switching an external control valve in accordance with a required operation in a state where the operation is performed by a number.
[0006]
It is another object of the present invention to perform control like a variable discharge pump with a constant discharge pump by opening / closing switching operation of a control valve.
[Means for Solving the Problems]
[0007]
In order to solve the above-mentioned problems, in the present invention, a drive source having a required amount of inertia inherently or added thereto, a hydraulic pump driven by the drive source, and a first connected to the discharge side of the hydraulic pump. A control valve, a flow path leading the passage side of the first control valve to the hydraulic oil tank, a check valve with the input side facing the discharge side of the hydraulic pump, and a pipe on the output side of the check valve A first energy storage device provided via a path, and a load connected to a pipeline branched from the pipeline between the first energy storage device and the check valve, A control circuit for switching the opening / closing operation of the control valve, Qm is the torque generated by the drive source 41, and the torque of the hydraulic pump when the first control valve is switched to the blocking side Qp, the moment of inertia around the axis of the drive source is 1, angular velocity Is ω, and the inertial torque of the drive source is I · dω / dt, the value of Qp exceeds the value of Qm in the relational expression of Qp = Qm−I · dω / dt, By repeating the operation of switching the first control valve between the passing side and the blocking side by the control circuit and causing the value of the angular velocity ω of the driving source to perform a self-excited oscillation operation, the rotational speed of the driving source is reduced. A hydraulic device that continuously supplies hydraulic fluid whose pressure has increased when the hydraulic pump is driven with a torque added to an output torque of the drive source to the load. Use as a means.
[0008]
In another embodiment, a rotation detecting means for detecting the number of rotations of the drive source is provided, and when the value of the rotation detecting means decreases to a lower limit set value, the control circuit causes the first on-off valve to pass through the first on-off valve. 2. The state is switched, and when the value of the rotation detecting means increases to an upper limit set value, the control circuit switches the first control valve to a blocking side state and repeats these operations. The described hydraulic device is used as means.
[0009]
In another embodiment, the control circuit includes a rotation detection unit that detects the number of rotations of the drive source, and determines the timing for repeatedly switching the first control valve according to the value of the rotation detection unit. 2. The hydraulic apparatus according to claim 1, wherein the first control valve is repeatedly switched between a passing side and a blocking side.
[0010]
In another embodiment, pressure detecting means provided on the output side of the check valve is provided, and when the value of the pressure detecting means increases to an upper limit set value, the control circuit controls the first control valve 1. When the value of the pressure detection means decreases to a lower limit set value, the first control valve is switched to the blocking state by the control circuit and these operations are repeated. The hydraulic device according to claim 1 is used as means.
[0011]
In another embodiment, the control includes pressure detecting means provided on the output side of the check valve, and determines the timing for repeatedly switching the first control valve according to the value of the pressure detecting means. 2. The hydraulic apparatus according to claim 1, wherein the first control valve is repeatedly switched between a passing side and a blocking side by a circuit.
[0012]
A second control valve connected to a pipe branched from a pipe between the first energy storage device and the check valve and provided with the load on the downstream side; and the second control valve And a check valve with the input side directed to the hydraulic oil tank in a pipe branched from the pipe between the load and the load, and repeatedly switching the second control valve between the passing side and blocking state 6. The hydraulic device according to claim 1, wherein the load is intermittently accelerated when the required oil amount of the load is greater than a supply oil amount of a hydraulic pump. Use as a means.
【The invention's effect】
[0013]
In the present invention, the hydraulic oil discharged from the constant pressure hydraulic power source can be efficiently supplied from the high pressure small flow rate to the low pressure large flow rate by switching the control valve according to the required load. A prime mover such as a heat engine or electric motor can be used in the vicinity of the most efficient rotational speed, and the driven hydraulic pump is always efficient regardless of the type, such as a constant discharge amount or variable discharge amount pump. Since it can be operated at a good rotational speed, the conventional element can be operated efficiently, and the efficiency of the entire system can be further increased.
[0014]
In addition, according to this operation, energy loss that has been discarded as surplus in the conventional constant discharge pump is also eliminated, so temperature rise and deterioration of the hydraulic oil can be prevented, and the operation as a variable discharge pump Since the pump can be realized without changing the capacity, the same function as the variable discharge pump can be realized by the constant discharge pump without using an expensive variable discharge pump.
[0015]
In addition, when the hydraulic device of the present invention is used as a drive device for a vehicle or the like, regenerative braking is realized by collecting the kinetic energy of a traveling vehicle or the like, or the prime mover that is a drive source functions as an engine brake. In the meantime, the reversible operation of the pump motor becomes free and high-efficiency operation is possible. Moreover, when it does not regenerate, the temperature rise of hydraulic fluid can be prevented.
BEST MODE FOR CARRYING OUT THE INVENTION
[0016]
FIG. 1 is a diagram showing a hydraulic circuit including components of a hydraulic device according to the present invention and a flow path connecting them. In FIG. 1, reference numeral 41 denotes a drive source, which is mainly a heat engine, but other types can also be adopted. An inertial body, specifically, a flywheel 45 is attached to the shaft 201 of the drive source 41, and the hydraulic pump 11 is driven by the shaft 202. If the drive source itself has a large moment of inertia, the external flywheel 45 can be omitted if the inertia is inherent. FIG. 1 shows the entire system of a hydraulic system, and a plurality of parts responsible for different functions and operations are organically coupled. Incidentally, the hydraulic pump 11 will be described later in the present hydraulic device, also constitutes a third pump motor Ru also functions of the motor.
[0017]
A pipe line 105 is connected to the discharge side of the hydraulic pump 11, and a branched pipe line 106 communicates with the pipe line 105 and operates via the control valve 1 constituting the first control valve of each claim. A conduit 107 leading to the oil tank 21 is connected. In the state where the drive source 41 is started and the hydraulic pump 11 is operating at a preset rotation speed, that is, at the set rotation speed, the hydraulic oil is supplied from the hydraulic oil tank 21 to the pipeline 101, the filter 22, the pipeline 102, and the reverse. The air is sucked into the hydraulic pump 11 through the stop valve 23 through a flow path that reaches the inflow side pipe 104 of the hydraulic pump 11.
[0018]
The suctioned hydraulic oil is discharged by the hydraulic pump 11, and flows from the discharge side pipe line 105 to the hydraulic oil tank 21 through the pipe line 106, the passage side 1 a of the control valve 1, and the pipe line 107. In a state where the control valve 1 is switched to the passage side 1a, an unload flow path is formed after the pipe line 106.
[0019]
In this state, when the control valve 1 is switched from the passage side 1a to the blocking side 1b, the hydraulic oil whose pressure has been increased by the hydraulic pump 11 driven by the drive source 41 passes through the pipelines 105 and 108 on the input side. Is passed through the check valve 24 that is connected so that the load is connected to the output side of the check valve 24. As described above, when the control valve 1 is switched from the passage side 1a to the blocking side 1b, the discharge pressure that can be continuously generated by the hydraulic pump 11 operated by the drive source 41 at the set rotational speed, that is, during the normal operation of the hydraulic pump 11 A pressure higher than the discharge pressure is generated.
[0020]
The drive source 41 is a prime mover such as a heat engine or an electric motor. When the torque that can be generated is Qm, if the torque of the hydraulic pump 11 driven by the drive source is Qp, Qm = Qp It is clear that this relationship holds. Here, if the inertia moment of the drive source 41 is I and the angular velocity is ω, the inertia torque required when the drive source accelerates or decelerates can be expressed by I · dω / dt. Note that I · dω / dt has a value of + when accelerating and − when decelerating.
[0021]
In the apparatus of the present invention, when the control valve 1 is in the state of the passing side 1a, the drive source 41 is controlled to maintain the set rotation. When the control valve 1 is switched to the blocking side 1b, the inertia torque I · dω / dt of the drive source 41 is added to Qm, and the relationship of Qp = Qm−I · dω / dt is established. Therefore, by adding inertia torque due to deceleration, an output torque larger than the input torque Qm of the hydraulic pump 11 during normal operation can be obtained, and as a result, hydraulic oil whose pressure has increased can be supplied to the load. .
[0022]
The description so far has been made only when the operation of switching the control valve 1 from the passing side 1a to the blocking side 1b is performed only once, but switching from the blocking side 1b to the passing side 1a and switching back to the blocking side 1b again. By repeating the operation (switching operation), high-pressure hydraulic oil can be continuously supplied to the load as described above.
[0023]
In this way, in the present invention, since a high hydraulic pressure can be supplied with a smaller drive source, it is possible to drive without providing a drive source having an output torque that matches the maximum load torque required by the load, There is a big economic advantage. The maximum pressure that can be generated can be set according to the moment of inertia I of the drive source 41 and the magnitude of the angular acceleration dω / dt.
[0024]
The switching operation of the control valve 1 is performed as follows. In FIG. 1, the flywheel 45 is provided with a tachometer 49, and the rotation speed of the drive source 41 is detected by this tachometer 49. A pressure sensor 33 is provided on the output side of the check valve 24. It can be detected by the tachometer 49 that the load torque of the hydraulic pump 11 exceeds the output torque of the drive source 41, and as a result, the rotational speed has decreased to the lower limit set value of the rotational speed.
[0025]
When the rotational speed becomes equal to or lower than the lower limit set value, the control valve 1 is switched to the passing side 1a to set the unload state, that is, the state where the load of the hydraulic pump 11 is removed. As a result, the load torque applied to the drive source 41 decreases, and the rotational speed gradually increases to the upper limit set value or more. At this time, the operation of switching the control valve 1 to the blocking side 1b is performed again. Needless to say, this switching operation can be performed at the moment when the set value is predicted to be reached either at the moment when the upper limit set value is reached or at a later time. In this way, the control valve 1 repeatedly performs the switching operation to maintain the self-excited operation. The speed of change of the rotational speed of the hydraulic pump 11, that is, the speed of change of the hydraulic oil discharge amount depends on the moment of inertia around the axis of the hydraulic pump 11.
[0026]
The pressure sensor 33 measures the pressure state on the output side of the check valve 24. When the measured value of the pressure sensor 33 reaches a predetermined set value, the control valve 1 is switched from the blocking side 1b to the passing side 1a, and the hydraulic oil discharged from the hydraulic pump 11 is returned to the hydraulic oil tank 21. By this operation, the load on the prime mover is unloaded, and the rotational speed increases. As described above, the sensor used for determining the switching timing is the detection means that constitutes each claim such as the pressure sensor 33 and the tachometer 49, the sensor that monitors the load state, and the switching timing is known in advance. In such a case, it is also possible to carry out according to the external clock timing without monitoring the state.
[0027]
On the output side of the check valve 24, a first energy storage device 31 provided via lines 109 and 110, and a pipe line 115 between the first energy storage device 31 and the check valve 24. , 116 and the control valve 2 constituting the second control valve of each claim, and a load 12 provided on the downstream side of the control valve 2. In the embodiment, the load 12 is the hydraulic motor 12 provided with the second energy storage device 42. As a specific device of the second energy storage device 42, a flywheel attached to the hydraulic motor 12 is used. It is. As will be described later, the hydraulic motor 12 also constitutes a second pump motor of each claim that also serves as a pump in the hydraulic apparatus.
[0028]
When the control valve 2 is switched to the passage side 2a, hydraulic fluid flows into the hydraulic motor 12 from the hydraulic pump 11 driven by the drive source 41 and the accumulator 31 as an energy storage device, and from the discharge-side pipe 124. The oil is returned to the hydraulic oil tank 21 via the control valve 4 in the middle of the pipe line leading to the branched hydraulic oil tank 21. By this operation, the flywheel 42 provided in the hydraulic motor 12 is accelerated.
[0029]
Between the control valve 2 and the hydraulic motor 12, pipes 120, 121, 122 provided with a check valve 26 connected to the hydraulic oil tank 21 with the input side directed are provided. The reason will be described with reference to FIG. FIG. 2 shows the main elements for explanation extracted from FIG. When the rotation speed of the hydraulic motor 12 increases and the required oil amount of the hydraulic motor 12 becomes larger than the supply oil amount of the hydraulic pump 11, the hydraulic motor 12 cannot be accelerated.
[0030]
At this time, the control valve 2 is switched from the passage side 2a to the blocking side 2b. By this operation, the hydraulic oil is accumulated in the accumulator 31, and the hydraulic motor 12 enters the freewheeling state by the check valve 26. When a predetermined amount of hydraulic oil is accumulated in the accumulator, when the control valve 2 is switched to the passage side 2a again, the accumulated hydraulic oil flows into the hydraulic motor 12, and the hydraulic motor 12 is accelerated. In this way, by repeating the switching operation of the control valve 2, even when the required oil amount of the hydraulic motor 12 is larger than the supplied oil amount of the hydraulic pump 11, acceleration can be intermittently performed. Therefore, although the acceleration average pressure is low, a large flow rate can be supplied to the load.
[0031]
Next, the case where the hydraulic device of the present invention is used as a vehicle drive device will be described. In FIG. 1, a check valve 27 connected to the discharge side of the hydraulic motor 12 with the input side directed through a pipe line is provided, and an accumulator 34 and a control valve 5 are provided on the output side. A pressure sensor 36 is also provided on the output side of the check valve 27. Between the pipes 128 and 129 on the output side of the check valve 27, pipes 160 and 161 having the control valve 6 communicating with the pipes 103 and 104 on the inflow side of the hydraulic pump 11 are branched and communicated. In addition, when the flywheel 42 is operating at a preset rotation speed, the control valve 6 supplies hydraulic oil to the pump motor 11 by the pump motor 12 by performing an opening / closing operation, and starts the drive source 41. Used to perform operations such as
[0032]
The 13 and 14 located downstream of the control valve 5 is a pump motor which constitutes the first pump motor, 43 and 44 connected to the pump motor 13 and 14, a simplified vehicle wheels or the like driven by these It is shown in the form. The control valve 7 to which the pump motors 13 and 14 are connected controls the traveling direction of the vehicle. Connected to the pipes 136 and 138 between the control valve 5 and the control valve 7 are pipes 117 and 118 provided to directly drive the vehicle from the drive source 41, the control valve 3 and the pipe 137.
[0033]
On the discharge side of the pump motors 13 and 14, a conduit 155 , a control valve 8 constituting a third control valve, and a conduit 157 are connected to return the discharged hydraulic oil to the hydraulic oil tank 21. A check valve 30 is connected to the pipe line 158 connected to the pipe line 155 with the input side directed.
[0034]
In the vehicle configured as described above, the start and acceleration operations will be described first. Since starting is when the initial speed of acceleration is zero, and acceleration gives acceleration force during running, both will be described simply as acceleration in the future. When accelerating the vehicle, only the drive source 41 is used, only the flywheel 42 operating at a preset number of revolutions is used, and both the drive source 41 and the flywheel 42 are used. There are three cases of cases.
[0035]
When the vehicle is accelerated only by the drive source 41, the control valves 2, 5, and 6 and the control valve 9 in the middle of the bypass line from the output side of the check valve 30 to the line 161 are set to the blocking side. When the control valve 8 is switched to the pass side 8a, the control valve 3 is fixed to the pass side 3a, and the control valve 1 is repeatedly switched to the pass side 1a and the blocking side 1b depending on the situation, When the valve 1 is fixed to the blocking side 1b, the control valve 3 is switched to the passage side 3a and the blocking side 3b repeatedly according to the situation, and both the control valves 1 and 3 are switched as necessary. There are three more cases. However, the control valve 5 can be switched according to the situation. Further, an acceleration operation can be performed even if a control valve not shown in the figure is arranged in the pipe line 138 and the same operation as described above is performed.
[0036]
When accelerating only with the flywheel 42, the flywheel 42 operating within a preset range becomes the driving side, and thereby the control operation when accelerating the vehicle on the driven side is at least a control valve 3 and 6 and 9 are set to the blocking side and the control valve 8 is set to the passing side 8a, the control valve 5 is fixed to the passing side 5a, and the control valve 4 is repeatedly set to the passing side 4a and the blocking side 4b depending on the situation. Same as the previous column when switching operation is performed, when the control valve 4 is fixed to the blocking side 4b and the control valve 5 is repeatedly switched operation, and when both the control valves 4 and 5 are repeatedly switched operation There are three cases.
[0037]
Further, even when the vehicle is accelerated by both the drive source 41 and the flywheel 42, it is possible by repeatedly switching the control valve according to the situation as described above.
[0038]
Here, the switching operation according to the state of the control valve will be described. Although the amount of hydraulic oil changes according to the speed of the vehicle, the amount can be determined by detecting the state of the driven pump motors 13, 14 and the like, and the amount of oil that can be supplied is also the driving side. This can be determined by detecting the rotational speed of the pump motor 11 or 12 or the like. When detecting the rotation state, the means for detecting each state includes a sensor 46 provided on the flywheel 42, sensors 47 and 48 provided on the pump motors 13 and 14, and a sensor 49 provided on the flywheel 45. Etc. Moreover, when detecting the state of hydraulic fluid, it is performed by the sensors 33, 36, etc. The switching operation is performed according to these detected values. The flow rate can be measured with a flow rate sensor or the like.
[0039]
For example, when the sensor 36 reaches a preset upper limit pressure, the control valve 4 is switched to the passing side 4a, and when the preset lower limit pressure is reached, the control valve 4 is switched again to the blocking side 4b, and this switching operation is performed. Accelerate by iteration. Thus, the acceleration can be controlled by changing the upper limit and lower limit pressure set values. In addition, when the states of the driving side and the driven side can be grasped in advance, the control valve can be switched by a control signal or a clock output from a separately provided control circuit.
[0040]
The hydraulic oil for accelerating the vehicle passes through the control valve 3 from the hydraulic pump 11 in FIG. 1 and flows into the pump motors 13 and 14, and is discharged to the hydraulic oil tank 21 via the passage side 8 a of the control valve 8. . In a state where the flywheel 42 attached to the hydraulic motor 12 is rotating, the pump motor 12 is operated as a hydraulic pump, and the accumulator 34 is accumulated from the hydraulic oil tank 21 via the discharge side pipe line. The hydraulic oil can be used for driving.
[0041]
Next, a case where the vehicle is in a coasting state will be described. In this case, if at least the control valves 3, 5 and 6 are on the blocking side and the control valve 8 is switched to the passing side 8a, the input side to the hydraulic oil tank 21 communicating between the pipelines 138 and 142 is connected. Pipe lines 139, 140, 141 provided with a check valve 29 connected in the direction serve as a freewheeling circuit for the pump motors 13, 14, and the hydraulic oil passes through the control valves 7, 8 to the hydraulic oil tank 21. Returned. In this state, the vehicle is in a coasting state. It is also possible to coast by using a control valve 7 other than the type shown in FIG. 1 and configuring the pump motors 13 and 14 as closed circuits.
[0042]
Finally, a case where the vehicle is decelerated will be described. There are two patterns of deceleration operations: a deceleration operation with regeneration and a deceleration operation without regeneration. First, the deceleration operation accompanied by regeneration will be described. The output side of the check valve 30 connected to the discharge side of the pump motors 13, 14 is connected to the input side of the control valve 2. As a result, the drive side becomes the pump motors 13 and 14, and the driven side becomes the second pump motor 12 that drives the flywheel 42, and the flywheel 42 is accelerated, which becomes a load and reduces the speed of the vehicle. Do. The control operation is the same as that when accelerating the vehicle from the flywheel 42. The control valve 5 and the control valve 4 to be switched become the control valve 2 and the control valve 8, respectively, and can be explained by performing the same operation.
[0043]
Next, the deceleration operation without regeneration will be described. FIG. 3 shows a circuit configuration necessary for decelerating the vehicle without regenerating kinetic energy, which is extracted from FIG. The operation in this configuration will be described. When the vehicle decelerates, the hydraulic oil discharged from the pump motors 13 and 14 flows into the pump motor 11 that operates as a motor. Since the pump motor 11 is connected to the drive source 41, it operates as a so-called engine brake and decelerates the vehicle. The control operation is the same as that in the case of accelerating the vehicle from the flywheel 42 described above, and the control valve 5 and the control valve 4 to be switched become the control valve 9 and the control valve 8, respectively, and perform the same operation. it can.
[0044]
The regenerative operation at the time of deceleration of the vehicle can be performed by the energy storage device or the flywheel described above. Even when regeneration is not particularly required, the hydraulic oil discharged from the pump motors 13 and 14 flows into the pump motor 11 and the prime mover connected to the pump motor 11 becomes a load and energy is consumed. Since it can decelerate without making it consume as heat energy with a valve etc., the temperature rise and deterioration of hydraulic fluid can be prevented.
[0045]
According to the present invention, the pump motors 11, 12, 13 and 14 can be operated by a constant discharge pump, and a reversible operation that cannot be realized by a variable discharge pump is also possible. The engine braking action of a prime mover etc. can be utilized now.
[0046]
Although the present invention has been specifically described based on the embodiments, the present invention is not limited to the above-described embodiments, and can be replaced as long as the elements satisfy the functions required by the present invention. .
[Brief description of the drawings]
FIG. 1 is a diagram showing components and a hydraulic circuit of a hydraulic device according to the present invention.
FIG. 2 is a diagram extracted from FIG. 1 and showing the configuration of an apparatus for operating the hydraulic pump of the present invention at a low pressure and a high flow rate.
FIG. 3 is a diagram extracted from FIG. 1 showing components and a hydraulic circuit in which the present invention is operated for deceleration of a vehicle or the like.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 thru | or 9 ... Control valve, 11, 12, 13, 14 ... Pump motor, 31, 34 ... Energy storage device or accumulator, 33 ... Pressure sensor, 41 ... Drive source or prime mover, 42 ... Flywheel, 45 ... Internal or external Additional inertial body, 46 to 49 ... tachometer

Claims (6)

所要量の慣性を内在または付加により具備した駆動源４１と、
この駆動源４１によって駆動される油圧ポンプ１１と、
この油圧ポンプ１１の吐出側に接続された第１の制御弁１と、
この第１の制御弁１の通過側１ａを作動油タンク２１へ導く流路と、
前記油圧ポンプ１１の吐出側に入力側を向けた逆止弁２４と、
この逆止弁２４の出力側に管路１０９，１１０を介して設けられた第１のエネルギ蓄積装置３１と、
この第１のエネルギ蓄積装置３１と前記逆止弁２４との間の管路から分岐された管路に接続された負荷と、
前記第１の制御弁１の開閉動作の切り替えを行う制御回路とを備え、
前記駆動源４１が発生するトルクをＱｍ、
前記第１の制御弁１が阻止側１ｂに切り替えられた状態にある場合の油圧ポンプ１１のトルクをＱｐ、
前記駆動源４１の軸周りの慣性モーメントをＩ、角速度をω、
および前記駆動源４１が有する慣性トルクをＩ・ｄω／ｄｔとしたときに、
Ｑｐ＝Ｑｍ−Ｉ・ｄω／ｄｔの関係式において、
Ｑｐの値がＱｍの値を超える値にあり、
前記制御回路により前記第１の制御弁１を通過側１ａ、阻止側１ｂの状態に切り替える動作を反復させ、
前記駆動源４１の角速度ωの値を自励振動動作させることで、
前記駆動源４１の回転数が減速することで得られる慣性トルクが、
前記駆動源４１の出力トルクに付加されたトルクで前記油圧ポンプ１１を駆動したときに圧力上昇した作動油を前記負荷に連続的に供給することを特徴とする油圧装置。A drive source 41 having the required amount of inertia inherently or in addition;
A hydraulic pump 11 driven by the drive source 41;
A first control valve 1 connected to the discharge side of the hydraulic pump 11;
A flow path for guiding the passage side 1a of the first control valve 1 to the hydraulic oil tank 21,
A check valve 24 with the input side facing the discharge side of the hydraulic pump 11,
A first energy storage device 31 provided on the output side of the check valve 24 via lines 109 and 110 ;
A load connected to a pipe branched from the pipe between the first energy storage device 31 and the check valve 24;
A control circuit for switching the opening and closing operation of the first control valve 1,
The torque generated by the drive source 41 is Qm,
The torque of the hydraulic pump 11 when the first control valve 1 is switched to the blocking side 1b is Qp,
The moment of inertia around the axis of the drive source 41 is I, the angular velocity is ω,
When the inertia torque of the drive source 41 is I · dω / dt,
In the relational expression of Qp = Qm−I · dω / dt,
The value of Qp is above the value of Qm,
The operation of switching the first control valve 1 to the state of the passing side 1a and the blocking side 1b by the control circuit is repeated,
By causing the value of the angular velocity ω of the drive source 41 to perform a self-excited vibration operation,
The inertia torque obtained by reducing the rotational speed of the drive source 41 is
A hydraulic apparatus characterized by continuously supplying hydraulic fluid whose pressure has increased when the hydraulic pump 11 is driven with a torque added to an output torque of the drive source 41 to the load. 前記駆動源４１の回転数を検知する回転検知手段４９を備え、
前記回転検知手段４９の値が下限設定値まで減少したとき前記制御回路により前記第１の制御弁１を通過側１ａの状態に切り替え、
前記回転検知手段４９の値が上限設定値まで増大したとき前記制御回路により前記第１の制御弁１を阻止側１ｂの状態に切り替え、
これらの動作を反復させることを特徴とする請求項１記載の油圧装置。A rotation detecting means 49 for detecting the rotation speed of the drive source 41;
When the value of the rotation detecting means 49 decreases to the lower limit set value, the control circuit switches the first control valve 1 to the state of the passing side 1a,
When the value of the rotation detecting means 49 increases to the upper limit set value, the control circuit switches the first control valve 1 to the blocking side 1b state,
The hydraulic apparatus according to claim 1, wherein these operations are repeated. 前記駆動源４１の回転数を検知する回転検知手段４９を備え、
前記回転検知手段４９の値に応じて前記第１の制御弁１の反復切り替えを行うタイミングを決定する前記制御回路により、
前記第１の制御弁１が通過側１ａ、阻止側１ｂの状態に反復切り替えさせることを特徴とする請求項１記載の油圧装置。 A rotation detecting means 49 for detecting the rotation speed of the drive source 41;
By the control circuit that determines the timing for performing the repeated switching of the first control valve 1 according to the value of the rotation detecting means 49,
The hydraulic apparatus according to claim 1, wherein the first control valve (1) repeatedly switches between a passing side (1a) and a blocking side (1b). 前記逆止弁２４の出力側に設けられた圧力検知手段３３を備え、
この圧力検知手段３３の値が上限設定値まで増大したとき前記制御回路により前記第１の制御弁１を通過側１ａの状態に切り替え、
前記圧力検知手段３３の値が下限設定値まで減少したとき前記制御回路により前記第１の制御弁１を阻止側１ｂの状態に切り替え、
これらの動作を反復させることを特徴とする請求項１記載の油圧装置。Pressure detecting means 33 provided on the output side of the check valve 24 ,
When the value of the pressure detecting means 33 increases to the upper limit set value, the control circuit switches the first control valve 1 to the state of the passing side 1a,
When the value of the pressure detecting means 33 decreases to the lower limit set value, the control circuit switches the first control valve 1 to the blocking side 1b state,
The hydraulic apparatus according to claim 1, wherein these operations are repeated. 前記逆止弁２４の出力側に設けられた圧力検知手段３３を備え、
前記圧力検知手段３３の値に応じて前記第１の制御弁１の反復切り替えを行うタイミングを決定する前記制御回路により、
前記第１の制御弁１が通過側１ａ、阻止側１ｂの状態に反復切り替えさせることを特徴とする請求項１記載の油圧装置。 Pressure detecting means 33 provided on the output side of the check valve 24,
By the control circuit for determining the timing for performing the repeated switching of the first control valve 1 according to the value of the pressure detection means 33,
The hydraulic apparatus according to claim 1, wherein the first control valve (1) repeatedly switches between a passing side (1a) and a blocking side (1b). 前記第１のエネルギ蓄積装置３１と前記逆止弁２４との間の管路１０９、１１０から分岐された管路に接続され、下流側に前記負荷１２が設けられた第２の制御弁２と、
この第２の制御弁２と前記負荷１２との間の管路から分岐した管路に作動油タンク２１へ入力側を向けた逆止弁２６とを備え、
前記第２の制御弁２を通過側２ａ、阻止側２ｂの状態に切り替える動作を反復させ、
前記負荷１２の必要油量が前記油圧ポンプ１１の供給油量より多いとき、
間欠的に前記負荷１２を加速することを特徴とする請求項１から５記載のうちいずれか１項に記載の油圧装置。 A second control valve 2 connected to a pipe branched from pipes 109 and 110 between the first energy storage device 31 and the check valve 24 and provided with the load 12 on the downstream side ; ,
A check valve 26 having an input side directed to the hydraulic oil tank 21 in a pipe branched from the pipe between the second control valve 2 and the load 12,
The operation of switching the second control valve 2 to the state of the passing side 2a and the blocking side 2b is repeated,
When the required oil amount of the load 12 is larger than the supply oil amount of the hydraulic pump 11,
The hydraulic apparatus according to any one of claims 1 to 5 , wherein the load 12 is intermittently accelerated.
JP2001356727A 2001-10-19 2001-10-19 Hydraulic device Expired - Fee Related JP3679749B2 (en)

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